Telegraph printer



Jan. 5, 1943. c. J. FITCH ETAL TELEGRAPH PRINTER Filed Nov. 18, 1941 5 Sheets-Sheet l ATTO R N EY Jan. 5, 1943. cl J. FITCH ETAL TELEGRAPH PRINTER Filed Nov. 18, 1941 5 Sheets-Sheet 2 R QN Y E N R O n A Jan. 5, 1943. c. J. FITCH ET AL TELEGRAPH PRINTER 5 Sheets-Sheet 5 Filed Nqv. 18, 1941 NW WW; J 5 Y W3; W E O wm mw Mm m M 8 .0

1943- c. J. FITCH ETAL 2,307,123

' TELEGRAPH PRINTER Filed Nov. 18, 1941 5 Sheets-Sheet 4 FIG. 6.

' ATTORNEY .Fan. 5, 1943. c. J. FITCH ET AL. 2507 3233 TELEGRAPH PRINTER Fild NCV. 18, .1941 5 Sheets-Sheet 5 TTORNEY Patented Jan. 5, 1943 TELEGRAPH IRINTER Clyde J. Fitch, Endweil, and Kurt R. Schneider,

Endicott, N. Y., assignors to International Business Machines Corporation, New York, N. Y., a corporation of New York Application November 18, 1941, Serial No. 419,575

7 Claims. (01. 197-49) The present invention relates to printing telegraphy and more particularly to a receiving printer wherein a message is recorded by impressing characters on a tape.

The invention embodies novel shift mechanism for directly and simply shifting the typewheel of a telegraph printer and for retaining the typewheel in the shifted position until reception of a shift signal requiring a further shift of the typewheel.

One of the objects of the present invention is to provide a novel simplified shift means for a telegraph printer whereby a typewheel is rotated in one direction or the other by a minimum n'umber of interengaging elements.

A further object is to provide novel simplified shift means which also serve to rotatably position the typewheel of a telegraph printer.

Still another object is to provide novel simplified shift means for finally rotatably shifting the typewheel of a telegraph printer and locking means for locking both said shift means and said typewheel. in either one of two assumed positions.

Other objects of the invention will be pointed out in the following description and claims and illustrated in the accompanying drawings, which disclose, by way of example, the principle of the invention and the best mode which has been contemplated, of applying that principle.

In the drawings:

Fig. 1 is a front elevational view, partly in section, illustrating the typewheel positioning mechanism.

Fig. 2 is a side elevational view, partly in section, illustrating the typewheel positioning mechanism and drive means therefor.

Fig. 3 is a top, plan view of the complete novel printer, including the tape feed mechanism.

Fig. 4 is a bottom, plan view, on an enlarged scale, of a portion of the novel printer.

Fig. 5 is a perspective view, on an enlarged scale, illustrating the'details of the clutch mechanism utilized in positioning the typewheel.

Fig. 6 is a sectional --view taken on line 6-6 of Fig. 4, and rotated QO-degrees counterclockwise.

Fig. 7 is a sectional fragmentary view, on an enlarged scale, taken on line 1-1 of Fig. 3.

Fig. 8 is a sectional fragmentary view, on an enlarged scale, taken on line 8-8 of Fig, 4.

Fig. 9 is an exploded view, on an enlarged scale,

illustrating the details of the shift mechanism Fig. 10a is a detail view illustrating a portion of the mechanism of Fig. 10.

Fig. 11 is a perspective view, on an enlarged scale, illustrating the details of the adjusting and operating mechanism for the printing hammer.

Referring to the drawings and more particularly to Figs. 1, 2, 3 and 4, the novel printer comprises a supporting frame (Figs. 2, 3 and 4) including a front panel 20a, a side frame member 20b and protruding semicircular front portions 20c.

A motor 2| (Fig. 3) carried by the frame 20 drives shaft 22 carrying the worm 23 meshing with worm wheel 24 carried by shaft 25 (Fig. 2). Shaft 25 is suitably journaled at each end in frame 20 and carries at one end thereof the fiber driving gear 26 (Figs. 1 and 2) for driving the mechanism controlling the rotative positioning of the typewheel. At its other end, the shaft 25 carries the fiber driving gear 21 for driving the mechanism that axially positions the typewheel.

By the mechanism just described, motor 21 drives shaft 25 at 900 R. P. M., which is not synchronous speed but is faster than the speed of the incoming signals.

Gear 26 meshes with gear 28 carrying a shaft 29 on which is mounted ratchet gear 3|].

Gear 21 meshes with gear 31 carrying a shaft 32 on which is mounted ratchet gear 33.

Gears and 33 are thereby driven at 1200 R. P. M. Gear 30 drives the eight position clutch mechanism 34, which in turn is controlled by permutation disk mechanism, all as described presently, to rotatably position shaft 35 and typewheel 36, while gear 33 drives the four position clutch mechanism 31, also controlled by permutation disk mechanism, to rotatably position the cylindrical cam member 38 which, as described later, by its rotative positioning controls the axial positioning of the typewheel.

Clutch 34 rotatably positions the typewheel 33 in any one of eight uniformly distributed rotative positions whereby any one of eight vertical columns of characters (Fig. 2) may be selectively positioned in printing position. Novel shift mechanism is also provided, as described later, to further rotatably position the typewheel 36, in

positions respectively intermediate each of these eight rotative positions, whereby the typewheel is selectively adjusted to alternate ones of two rotative positions corresponding to each of the above eight rotative positions.

Gear 21 (Fig. 2) also meshes with gear 39 carrying a shaft 40 on which is mounted ratchet gear 4| for driving the clutch 42, which clutch is controlled by single revolution mechanism, de scribed later, to permit rotation of shaft 43 under the control of clutch 42 for one complete revolution only. Shaft 43 carries a plurality of cams, so distributed circumferentially of shaft 43 as to operate in proper time sequence, the ribbon feed, tape feed, printing hammer cocking and release mechanism, restoring mechanism and shift mechanism of the novel printer, all as described in detail later.

Clutch mechanism The clutch devices 34, 31 and 42 may be of the type, as fully shown and described in Patent No. 2,206,646, granted to Kurt R. Schneider July 2, 1940. Referring to Fig. 5, there is illustrated therein the construction of such a clutch, which in the particular instance, may be rotatably positioned in any one of four different positions (such as clutch 31 of Fi 2) but it is to be understood that the construction of each of the clutches 34, 31 and 42, respectively, is the same, with the sole exception of the number of rotative positions to be assumed by the clutch. As illustrated in Fig. 5, the clutch comprises a cylindrical member 44 provided with a series of four notches 44n distributed about a flange member 44a integral with member 44. A shaft portion 441), also integral with member 44, is provided, which internests with the associated driven member, as described later, to transmit the rotation of the member 44 to the associated driven member and thereby rotatably position the. driven member similarly to the rotative positions assumed by member 44. A pivoted pawl member 45 (see also Figs. 4 and 6) is urged by spring element 46 into engagement with the flange member 44a to cooperate with a notch 441i and thus prevent back rotation of the clutch, when stopped in any one of its four positions. The face 44! of member 44 of the four position clutch illustrated in Fig. 5, is located adjacent its cooperating ratchet gear 33 (see also Fig. 1), driven by shaft 32, as described above. A channel 440 is provided in face MI, in which channel is slldably mounted a dog member 41 provided with an axially extending tooth 41t which also extends radially towards the toothed periphery of ratchet gear 33. A member 44d, integral with member 44, extends axially into the channel 440, as shown in Fig. 5 and also part way diametrically of member 44. A spring member, as disclosed in said Patent No. 2,206,646, abuts member 44d and spring biases member 41 so that the tooth lit tends to engage the teeth of ratchet gear 33. A dog lift lever 48 (see also Fig. 4) is pivoted by its ball-shaped end 48p fitted into a socket in the face 44), and extends crosswise of dog 41 and engages dog 41 with its center portion. The other end of lever 48 is cut diagonally to form a tooth 48f projecting beyond the circumference of member 44. A slot 44s is formed in the face of member 44, generally at right angles to channel 440, to permit oscillation of dog lift lever 48 with respect to 44, about the ball and socket connection, when 48t is engaged by a stop member 49 controlled by the permutation disk members, as described later. This oscillatory movement of lever 48 is transferred to dog 41 to move the dog, longitudinally of itself against the force of its biasing spring, and into the position as illustrated in Fig. 5. When a stop member 49 is moved radially to release tooth 48t, lever 48 will thereupon permit dog 41 to be moved to the left, as viewed in Fig.

5, under the influence of its biasing spring, to 76 thereby engage tooth 41t and associated ratchet gear 33, whereby the rotation of gear 33 is transmitted to member 44 and shaft 44b.

Typewheel positioning Novel means are now provided for completely positioning the typewheel, which comprise means for rotatably positioning the typewheel, means for axially positioning the typewheel and means for zone positioning or shifting the typewheel, which zone positioning comprises rotatively positioning the typewheel intermediate each of the eight assumed rotative positions mentioned above, to determine which character out of two primary groups of characters will be printed. These three sets of means will now be described in detail.

Rotative positioning of the typewheel As illustrated in Figs. 3 and 4, a plurality of five permutation magnets and also a printing magnet are provided. Each of the five permutation magnets is responsive to one element of a 5-unit code signal received. Three of the magnets 50, 5| and'52 (Fig. 3), controlled, respectively, by the first, second and fifth code signal elements, are utilized to control permutation disk or ring members which in turn regulate the rotative positioning of the typewheel. Two of the magnets 53 and 55 (Fig. 4) controlled, respectively, by the third and fourth code signal elements are utilized to control the permutation ring members which in turn regulate the axial positioning of the typewheel. The print magnet 54 controls mechanism for regulating the rotation of clutch 42 to produce a single revolution only, of clutch 42 and its associated shaft 43, which in turn controls the zone positioning of the typewheel and also controls, in proper sequence, the tape and ribbon feed, the print hammer cooking and releasing functions and the reset functions. When sequential, code signal elements are utilized, as may be assumed in the instant application, print magnet 54 is controlled by the stop element of the permutation of code elements of a full complete signal which complete signal when the 5-unit code is utilized comprises a start element, five code signal elements proper, and a stop element.

Referring to Figs. 3 and '7, there is illustrated the permutation means associated with clutch 34 for selectively rotatively positioning the typewheel. As is seen in Fig. 3, clutch 34 is stopped by engagement of tooth 48t of its dog lift lever 48 with a tooth 49t of a stop member 49 (Fig. 5). Each stop member 49 is provided with a laterally projecting support member carrying its tooth 49t and also with a laterally extending support member carrying projection 49p (see also Fig. 4) which cooperates with notches in the permutative members, as described presently. The laterally extending support members for 49t and 4911 provide a channel 49c. Eight such stop members 49 are distributed circumferentially about clutch 34. A set of three permutation selector rings 55, 51 and 58 (Fig. 7) are disposed coaxially with clutch 34, the annular portion of the rings being located within each of the channels 49c of the eight stop members, respectively. These rings are maintained in position, coaxial with clutch 34, by a projecting circular front portion 200 of casing 20 (Fig. 3) and by the eight stop members 49, distributed circumferentially of the permutation ring members. Each of the stops 49 is mounted for movement radially of the annular permutation members and is constantly urged toward thecenter of the annular members by means of an individual spring 49s. Each of the three permutation rings is held against bodily lateral movement by means of a member 59 (see also Fig. 6) provided with an annular channel 590 in which the rings are located. Member 59 is also provided with a series of radially extending openings 581 in which are located the respective stops 49. An annular cover plate 60 serves to hold the rings in place within the channel 59c and a plurality of ball members 60a serve as antifriction members for rotatively mounting the respective rings. I

Each of the rings 56, 51 and 58 may be rotated by means of a lever 6| (Fig. 3) pivoted at 6 Ip and biased by spring 6 Is for counterclockwise rotation. A lug 6|a on lever 6| is pivotally connected to its corresponding permutation ring (ring 56, for example) whereby the ring is rotated clockwise upon counterclockwise rotation of lever 6|. Each lever 6| is maintained in the cocked position, as

illustrated in Fig. 3, by a trigger element 62,

pivoted at 62p and biased by spring 62s for clockwise rotation. A lug 62a on trigger 62 engages a shoulder 6| on lever 6| to hold the lever 6| in cocked position. A link 63 is pivotally attached to each trigger 62 and is also pivotally connected to a pivoted armature 64, one for each of the magnets 50, and 52, respectively (Fig. 3), V

and likewise one for each of the magnets 53, 54 and 55 (Fig. 4). Upon energization of any magnet, its associated armature 64 is rotated clockwise (as viewed in Fig. 3) to move the link 63, to the left, to rotate trigger 62 counterclockwise, to thereby release the cocked lever 6| for counterclockwise rotation under the influence of its spring 6| s, which furnishes the motive power to in turn rotate the associated ring clockwise. It is obvious that only a short, relatively weak signal is required to actuate the magnets and thereby the rings, since the work required to rotate the rings is actually performed by the springs 6|s, the magnets merely controlling the trigger elements.

The relative rotation of the rings 56, 51 and 58 aligns a single set of individual notches 65 (Fig, 4) formed in the outer peripheries of the respective rings. Since each ring can be operated to any one of two positions and since there are three rings provided, a total of eight permutative positions may be obtained. Each of the three rings (Fig. 7) is therefore provided with eight notches (as compared to the four notches as illustrated in Fig. 4) the notches on the respective rings being so positioned relatively to each other that a plurality of three notches, and three only;

one only on each of the rings respectively; will be aligned for each of the eight rotative positions of the three rings, and such alignment occurs directly beneath one only, of the resiliently biased stops 49 cooperating with these three rings. The projection 49p of the particular stop, thus selected, will enter the three aligned notches of the three rings, respectively, while any previously aligned stop will be cammed out of its cooperating notches, and all of the stops, except for the one now aligned, are held in their most remote radial position by the outer peripheries of the three rings.

A different stop is, therefore, permitted to move radially inward for each of the eight permutation positions of the three rings.

Furthermore, the notches on the respective rings are so arranged, that clutch 34 will be rotated to any one of its several assumed positions,

in the least possible time. For example, it may be assumed, as stated above, that under ordinary sequential code signal element operation, magnets 50, 5| and 52 (Fig. 3) are energized by the first,

second and fifth actual code signal elements, re-

spectively, of a five element code. Upon energization of magnet 52, ring 58 will be released and that stop member 46, now illustrated in Fig. 3 as engaging dog lift lever 48, will becammed out of its associated notches 65, by point 49p riding up the sides of the notches as the ring 58 is rotated clockwise, and dog lift lever 48 will therefore be released. The notches of the three rings 56, 51 and 58 are so chosen and arranged, that when magnet 52 only, is energized, and ring 58 only is rotated, the immediately adjacent stop, in a counterclockwise direction from the stop now illustrated as engaging lever 48 in Fig. 3, will be aligned with three notches in the respective rings 56, 51 and 58. Therefore, when dog lift lever 48 is released from the position, as shown in Fig. 3, dog 41 (Fig. 5) of clutch 34 is moved by its spring to engage tooth 4'lt and the associated rotating ratchet gear 38 of clutch 34 (Fig. 2). Clutch 34 is thereupon rotated until dog lift lever 48 (Fig. 3) engages tooth 49tof the immediately adjacent stop 49, and the clutch is thereby stopped after having completed one-eighth of a revolution. If magnet 5| only, is energized, ring 51 only, is released for rotation and clutch 34 will rotate onequarter of a revolution from the position as shown in Fig. 3. If magnet 5| is first energized and magnet 52 is sequentially energized, the clutch will be permitted to rotate three-eighths of a revolution. If magnet 56 alone is energized, the clutch will be permitted to rotate a full half revolution. If magnets and 52 are both energized, the clutch will be permitted to rotate five-eighths of a revolution, if magnets 53 and 5| are both energized the clutch will be permitted to rotate siXth-eighths of a revolution and if magnets 50, 5| and 52 are all sequentially energized, the clutch will be permitted to rotate seven-eighths of a revolution. It is seen, therefore, that upon sequential operation of the magnets 58, 5| and 52, the clutch 34 will always advance to its selected position in the shortest possible time. This is likewise true of magnets 53 and and their associated clutch 31 (Fig. 4).

Novel means are also provided whereby all of the levers 6| associated with magnets 50, 5|, 52, 53 and 55 are reset to cocked position, as illustrated in Fig. 3, following the reception of each group of code signal elements comprising one complete signal and lever 6|b associated with print magnet 54 is also reset. Upon release of the single revolution clutch 42 (Fig. 2), as described presently, shaft 43 is allowed to rotate one single complete revolution. During the rotation of shaft 43, a reset carn66 (Figs. 2 and 3) carried by shaft 43 for rotation therewith is engaged by a roller 6'! on reset lever 68 (Fig. 3) which roller is continually'biased against the cam 66 by means of spring 68s acting on lever 68. Upon this rotation of cam 66, the reset lever is rotated clockwise, as viewed in Fig. 3, and a lug 68b integral with reset lever 68 engages the sides of notches 6|n formed in each of the three levers 6| (Fig. 3) to rotate these levers clockwise about their pivots against the force of their respective springs 6|s until the levers are restored to cocked position and locked by the triggers 62, as illustrated in Fig. 3. Levers 6| and 6|b (Fig. 4) associated with magnets 53, 54 and 55 are similarly reset by cam 66a, roller 61a and lever 68a with its lug 66c. Continued rotation of cam 66 permits the lever 68 to rotate to the position, as shown in Fig. 3, so that rings 56, 51 and 58 are free to rotate when the triggers 62 are released and levers 6| are operated. Restoration of the rings again aligns that particular stop 43, as illustrated in Fig. 3, to permit clutch 34 to rotate until dog lift lever 48 engages the tooth 4922 of stop 49, in the position as illustrated. It is to be noted that the clutch 34 during this last portion of its movement, moves counterclockwise or in the same direction as during its previous operation, so that the restoration of the clutch 34 and its controlled shaft 35, which determines the rotative position of the typewheel 36, is always in the same direction. It is seen, therefore, that the clutch 34 can assume any one of eight rotative positions, determined by the permutations of code signal elements received, and is returned to a chosen normal position after reception of each complete code signal. Similarly clutch 31 can assume any one of four positions, and is returned to a chosen normal position while clutch 42 is limited to one complete revolution.

As illustrated in Fig. 5, each clutch is provided with a shaft 44b integral with the clutch body 44. Shaft 44b of clutch 34 (Fig. 1) is inserted in an axial opening in the shaft 35 and is connected to the shaft for rotation thereof by a pin 35p. Upon rotation, therefore, of clutch 34, to any one of its eight positions, this rotation is transmitted to shaft 35.

A lower end of shaft 35 is reduced in diameter I and passes through bracket 69 attached to the with a pair of axially extending key ways 35k,

35k. A grooved collar member 16 (see also Fig. 9) is provided with radially inwardly extending lugs extending into the key ways 35k, respectively, whereby the "rotation of the shaft 35 is transmitted to member 10, but with member 10 free to move axially of shaft 35. Integral with collar 10 is a disk-10d provided with opposite, radially extending slots 16s, 163 (Fig. 9). A cylindrical member lilo, also integral with collar iilfextends axially of and surrounds the shaft (Figs. 1 and 9). A circumferentially extending groove 'lflg (Fig. 9) formed in the end of member 10c provides a bearing race for the ball bearings 36?) (Fig. 1) which also engage a race formed in the interior of typewheel 36, to provide an antifriction mounting for the typewheel, so that the typewheel can be easily rotated, with respect to shaft 35, as described presently. 'Iypewheel 36 is also provided with an axially extending opening in which is inserted a spring H and a retaining ball 12. The end of the axially extending opening in typewheel 36 is smaller than the diameter of the ball so that'only a portion of a hemisphere of ball 12 extends externally of the bottom face of typewheel 36 (Fig. 1). A radially slidable, zone selection or shift member 13 (Fig. 9) is mounted on cylindrical member 10c by means of an elongated or elliptical opening 13a formed in the slide 13. Slide 13 is provided on one face with a pair of projecting lugs 1317!, 13b2, disposed on opposite sides diametrically of slide 13, which lugs fit into and abut th sides of slots 10s when member I3 is mounted in position on member 160, as illustrated in Figs. 1, 2 and 10. The opposite face of slide 13 is provided with a cylindrical operating lug which rides in and engages the sides of a slot 14 (Figs. 9 and 10). Upon radial movement of slide 13 in such a direction that operating lug 130 is moved radially inward, the lug engaging the sides of groove 14 will rotate the typewheel 36 one-sixteenth of a revolution in one direction, while upon movement of slide 13 radially, in such a direction that lug 13c moves radially outward, the typewheel 36 is rotated in the opposite direction one-sixteenth of a revolution. A single lug 13c only, cooperates with a single groove 14 only, and serves to rotate the typewheel in either one of two required directions. A pair of indentations 13c, He, is provided on the same face of slide 13 as operating lug 130 (Fig. 9) adjacent the typewheel 36. Upon radial movement of slide 13 in one direction, ball 12 engages one indentation, and upon radial movement in the opposite direction, ball 12 engages the other indentation, to thereby retain slide 13 in either of its assumed positions. Ball 12 and the indentations 'l3e also serve to retain the typewheel 36 in one or the other of its rotative positions with respect to shaft 35. An abutting lug 13b, for cooperation wtih shift operating mechanism, to be described presently, is also provided on this same face.

As is seen in Fig. 2, typewheel 36 is provided with sixteen vertically extending columns of characters, each column comprising alternately figures and letters characters. By rotation of the typewheel 36 under control of shaft 35 and clutch 34, any one of eight uniformly, circumferentially distributed columns of characters is selected, and upon further rotation of the typewheel one-sixteenth of a revolution, with respect to shaft 35, one of two adjacent columns of characters, namely figures or letters," is chosen, so that the final rotative positioning of the typewheel with respect to shaft 35 is a zoning or shift function. This zoning or shift function will be described in detail presently, and is produced by engagement of shift operating mechanism with the abutting lug 73b (Fig. 9) or the lug l3bl, which last lugserves the dual purpose of an abutting and a guiding lug.

Novel means for axially positioning the typewheel will now be described.

Axial positioning of typewheel The two magnets 53 and 55 (Fig. 4) and the associated permutation ring members 15 and 76, which are similar to the ring members 56, 51 and 58, described above, control mechanism which in turn controls the axial positioning of the typewheel. Magnets 53 and 55, respectively, control the rings I5 and 16 by means of armatures 64, links 63, triggers 62 and pivoted levers 6!, in the same manner as magnets 50, 5i and 52 control their respective rings 56, 51 and 58. Relative rotation of rings 15 and 16 selectively aligns their notches 65 in difierent permutations, so that the four stops 49 (Fig. 4), cooperating with rings 15 and 16, may be selectively rendered effective, and the dog lift lever 48 of clutch 31 can be selectively positioned at any one of four different rotative positions and in the shortest possible time. The control of clutch 31 is, therefore, the same as that of clutch 34 with the sole exception that clutch 31 can be stopped in only four different positions instead of the eight of clutch 34.

The permutation disks l and 16 are reset to their normal positions under control of their associated levers 6|, by means of cam 660. (Fig. 2),

roller 81a, lever 68a and lug 680 in the same manner as the permutation disks 56, 51 and 58 are reset by means of their associated cam 66, roller 61 and arm 68, all as described above.

A plurality of four notches 4411. (Fig. 5) cooperates with pawl 45, as stated above, to prevent back rotation in any one of these four positions.

Similarly, as seen from'Fig. 4, the magnet 54, which may be designated as the print magnet, controls its trigger 62 by means of its associated armature 64 and link 63. Trigger 62 of the print magnet 54 controls a pivoted lever 6|b, generally similar to the levers 6|, and pivoted for rotation about pivot 6|p. Lever 6|b, however, is not attached to any permutation ring member but projects into the path of rotation of the dog lift lever 48 of clutch 42, and is held in position to .intercept the lever 48, by coaction with its trigger 62. Upon energization of print magnet 54, its trigger 62 releases lever 6) for rotation clockwise under control of its associated spring 6|s until .the end of lever 6|b is moved out of the path of rotation of lever 48, and the single revolution clutch 42 is released for rotation. Also, lever 6|b is reset to the position, as indicated in Fig. 4, by means of the reset cam 66a, roller 61a, reset arm 68a and lug 68c employed in resetting the permutation disks 15 and 16. The cam 66a (Fig. 2) is so positioned on shaft 43, controlled by the single revolution clutch 42, that the permutation disks 15 and I6 and the lever 6|b, are reset prior to completion of one complete revolution of clutch 42, so that lever 6|b is returned to the position, as illustrated in Fig. 4, in time to intercept the dog lift member 48 and halt the lever 48 in the position, as shown; to thereby terminate the single revolution of clutch 42. The shaft 44b (Fig. 5) of clutch 42 is inserted into an opening in the shaft 43 (Fig. 2) and is connected to the shaft 43 by a pin connection 43a.

The shaft 44b of clutch 31 (Fig. 1) is inserted into the axial opening 38a of cylindrical cam member 38 (Fig. 1) and is'attached to cam member 38 by pin 38p so that the rotation of clutch 31 is delivered to the cam member 38 to rotatably position the cam member in any chosen one of four possible positions. Cam member 38 is provided with a cam groove 389. A thick} roller 11 engages the sides of cam groove 389, as seen in Fig. l, and means are provided whereby roller 11 is moved up and down, or axially of shaft 35, upon rotation of cam member 38. A thick plate member I8 is attached by screws 19 to the front panel 26a. Cut into the edge of plate 18, adjacent the cam element 38, is a large groove 18g| (Fig. 2). In the opposing side walls of groove l8g| there are also cuttwo pairs of small guide grooves 'I8g2, the respective grooves of each pair being aligned in the direction of the thickness of plate 18. A plurality of thin rollers 80, of slightly larger diameter than roller TI, is carried by a member 8| and these rollers ride in the grooves 1892, to provide an antifriction mounting for the member 8| and to retain it within the large groove |8g| of plate 18. Roller I1 is also attached to member 8| and upon rotation of the groove 38a. The upward and downward motion of roller 11 is transmitted to member 8|, which also carries a second roller Ila, similar to roller 11, adjacent its upper end (Fig. 1); Roller Ila is located within the groove 16g of the grooved collar 16, which collar, as stated above, is mounted for rotation with shaft 35 but is free to move axially thereof. Roller Ila transmits the axial movement of roller 11 and member 8| to the collar 10. Since, as described above, the collar 10 is integral with disk 'llld (see also Fig. 9) while 10d and slide 13 carry the typewheel 36, the typewheel is selectively positioned axially, in any one of four chosen axial positions upon rotation of cam member 38 and consequent axial movement of member 8|. As is seen from Fig. 2, typewheel 36 is provided with four horizontal rows of characters extending circumferentially aboutthe periphery of the typewheel so that any one row can be chosen by the axial positioning of typewheel 36. By the rotative positioning of the typewheel under control of clutch 34, as described above, any one of eight circumferentially, uniformly distributed vertical columns of characters can be selected. It is therefore seen, that by the combined axial and rotative movement of typewheel 36, any one character, out of any one of eight vertical columns of characters, can be selectively located in position for printing. In order, however, to select one of two characters out of one of two adjacent vertical columns, novel shift or zone positioning mechanism is provided, which will now be described.

Zone positioning or shift Novel means are now provided cooperating with means on the typewheel, previously described, for producing zone positioning or shift. In one extreme axial position of the typewheel, the zone positioning or shift slide element 13 is so located axially and also oriented circumferentially that the shift operating mechanism can radially shift slide 13 to rotate the typewheel onesixteenth of a revolution in one direction, which operation comprises one shift function of the typewheel from letters" to figures or vice versa. In the other extreme axial position of the typewheel, slide 13 is so located axially and also circumferentially that the shift operating mechanism can rotate the typewheel one-sixteenth of a revolution in the opposite direction, which comprises the other shift function.

As described above, slide 13 is mounted for radial movement by means of the lugs 13b| and BM (Fig. 9) cooperating with slots 18s in member 10d. A single operating lug is also provided, as described above, cooperating with the sides of the slot 14 in the typewheel 36 to rotate the typewheel one-sixteenth of a revolution, either in one direction or the other depending upon the direction of movement of slide I3. When the shift operating mechanism cooperates with lug 13b| to move slide 13 so that operating lug 13c is moved radially inward,'the lug 13c cooperates with the sides of 'slot 14 to rotate the typewheel in one direction and when the shift operating mechanism cooperates with the abutting lug 13b to move slide 13- so that operating lug 13c is moved radially outward, the typewheel 36 is rotated one-sixteenth of a revolution in the opposite direction.

As shown in Figs. 2 and 10, a pair of shift operating levers 82 and 83 is provided. When standard teletype shift signals are employed, the figures signal places the typewheel 36 in its extreme lower position, asviewed in Fig. 2, while the letters" shift signal placesthe typewheel 36 in its extreme upper position. Lever 82 cooperates with lug 'I3bI, in the extreme lower position of typewheel 36, to radially move slide I3 so that lug 130 is moved radially inward to rotate typewheel 36 and perform the "figures" shift function. Lever 83, on the other hand, cooperates with abutting lug 13b, in the extreme upper position of typewheel 36, to move lug 13c radially outward and thus rotate typewheel 36 to perform the "letters shift function.

As is seen in Fig. 10, levers 82 and 83 areeach pivotally mounted for oscillation about pivots 82p and 83p, respectively.

An elongated slot 83s is formed'in lever 83. Spring 84, attached at one end to 8. lug 85 firmly fixed to the frame 20, is hooked at its other end to lever 83 and urges lever 83 to the position, as shown in Fig. 10, with the pivot 83p engaging the wall at one end of slot 83s. If, for any reason, lever 83 is prevented from rotating about pivot 83p upon operation of its operating cam, as described presently, lever 83 and slot 83s are moved to the right, as viewed in Fig. 10, and against the force of spring 84 whereby breakage of the lever 83 is prevented. Lever 82 is similarly resiliently mounted on pivot 82p. Further, levers 82 and 83 are respectively mounted for movement axially of pivots 82p and 83p, respectively, and against the force of associated springs 82a and 83a (Fig. 2) so that the levers 82 and 83 are further protected against breakage due to strain.

Each of the levers 82 and 83 is provided with an operating lug 82b and 83b, respectively (Fig. 10) 43 for rotation therewith, is provided with a pair of oppositely extending cam rollers 86a and 86b, cooperating respectively with lugs 82b and 83b of the shift operating levers 82 and 83. As shaft 43 is rotated, cam 86 rotates its cam rollers 86:: and 86b to simultaneously engage the lugs 82b and 83b, respectively, to simultaneously oscillate levers 82 and 83 about their respective pivots.

Upon reception of the figures shift signal, the typewheel is positioned in its extreme lower position, so that upon oscillation of lever 82, its operating end 820 will engage lug 'I3bl (Fig. 9) of slide 13 to radially move this element and thereby rotate typewheel 36 one-sixteenth of a revolution in one direction, as described above, to perform the figures shift function. On the other hand, upon reception of the letters" shift signal, typewheel 36 is located in its extreme upper position, and the operating end 830 of lever 83 will engage the cylindrical abutting lug 131) (Fig. 10) of slide 13 and the typewheel 36 will be rotated one-sixteenth of a revolution in the opposite direction, to thereby perform the letters" shift function.

Tape feed Novel tape feeding and tape guiding mechanism, as shown and described in applicants copending application Serial No. 419,576 filed November 18, 1941, is provided for feeding the tape, step by step, past the printing position and for guiding the tape. A roll of tape 81 (Fig. 3) is mounted within the tape roll support 88 attached to frame 20 by a bolt 88a and slotted link 88b. Tape 81 unwinds from its roll and passes under a guide roller 89 to a printing hammer support member 90 and within the upper tape guide slot 90a (Fig. 10), beneath a novel arcuate-shaped tape guiding member, described presently, and around the end 90b of the hammer support 90, and into lower guide slot 90a and tape guide 9| A cam 86 (Figs. 2 and 10) mounted on shaft W (see also Fig. 1), across the front panel 20a of the printer, so that as the characters are printed by the printing mechanism, the printed characters appear immediately in easily readable position on the face of the printer. Tape 81 (Fig. 3) is then fed between the knurled feed rollers of the novel tape feeding mechanism, which will now be described.

Mounted on shaft 43 for rotation therewith is an eccentric disk cam 92 (Figs. 2 and 3) provided with a peripheral, and radially extending slot 93 (Fig. 2). An unequal Y-arm lever 94 pivoted at 943) is provided with a short arm 94a and a long arm 94b fitting into the slot 93 in the disk cam 92 and embracing the small eccentric center of this cam (Fig. 3). Long arm 94b is pivotally connected, adjacent its free end, to a link 95 for operating the tape feed device. A lever 96 is integral with the eccentric three point star member 96a mounted for oscillation about shaft 91 joumaled in member 98 attached to the front panel 20a by pivot 96p. A series of holes 96b are provided in lever 96 whereby the connection of link 95 to lever 96 can be varied, to change the amount that the tape is fed for each oscillation of lever 96. In this manner, the spacing of the characters on the tape can be varied at will.

Lever 96, upon oscillation in a counterclockwise direction, similarly oscillates eccentric 96a. Balls 99 located between the outer periphery of member 96a and an inner race I00 of gear IOI, mounted freely on shaft 91, lock the member 96a and race I00 together upon such counterclockwise rotation, due to the eccentricity of the periphery of member 96a. Balls I00 are constantly urged towards engaging position by the spring elements I00a abutting the straight ledge portion of the fingers, respectively, of member 96a. Upon the return stroke, in a clockwise direction, of lever 96, the balls I00 no longer wedge together eccentric member 96a and the race I00 of gear MI, and gear IOI will not be rotated in the opposite direction. It is seen, therefore, that upon each complete back and forth stroke of link 95, the gear IOI will be rotated at predetermined amount in a counterclockwise direction only. Gear IOI meshes with gear I02, mounted for rotation on frame member 98, which gear I02 carries a pair of knurled rollers I03 (only one shown in Fig. 3) engaging the tape 81. Gear I02 meshes with gear I04, suitably mounted for rotation, on panel 20a, and carrying another pair of knurled rollers I05 (only one shown) aligned respectively with the knurled rollers I03, so that the feed rolls are rotated to feed the tape past the printing position, the amount of tape feed, and the spacing of the characters on the tape, being determined by the particular connection between link 95 and lever 96, as described above. The tape 81 can also be pulled by hand to feed the tape past the printing position, since this action rotates gear IOI counterclockwise, so that the balls 99 do not lock with eccentric member 96a.

Frame 38 pivoted at 981:, as stated above, and is urged constantly counterclockwise by spring 98s so that the respective knurled feed rollers I03 are held tightly in engagement with the tape 81 and force the tape 81 tightly into engagement with the respective rollers I05. To feed a new tape, frame 98 can be forced clockwise, against the force of spring 98s, to release the pressure between the knurled rollers I03 and I05.

As is seen from Fig. 10, the. end 901; of the printing hammer support, provides a sharp turning bend for the tape. To guide the tape around shoulder II2c (Figs. 10 and 11) which engages the end b when the tape is being threaded into position, a novel tape guiding member is provided. An arcuate-shaped member I08 (Fig. 10)

is attached to member I01 pivoted at I0Ip and provided with a finger operating portion I0'Ia. A spring l0ls is attached to the printing frame 90 at one end and to member I0l at the other end to bias the tape guide member I06 to the position, as shown in Fig. 10'. When a tape is inserted into the upper tape guide slot 90a and fed to the right, by hand, member IOTa is urged manually to the left, to rotate the arcuate member I06 clockwise to a position between the end 90b of' member 90 and the typewheel 36. The arcuate member thereby serves as a guide to thread the tape around the sharp bend of end 90b of member 90 and into the lower guide slot 00a of member 90 and the tape guide 92 on the front panel of the printer. Member 'I0la is thereupon released and assumes the position, as shown in Fig. 10, and tape 81 (Fig. 3) is fed by hand between the knurled rollers I03 and I05; by clockwise rotation of frame 98, as described above. The tape is then ready for automatic feed under control of the tape feed mechanism as controlled in turn by the rotation of shaft l3.

Ribbon feed and ribbon reversal mechanism I08 (Fig. 3) is provided, which may be of the type as shown and described in applicants copending application Serial No. 354,035, filed August 24, 1940, to which reference may be had for a more detailed description. The ribbon feed mechanism is operated by link I09 (Fig.3) connected 'to the long arm 94b of the unequal Y- arm operating lever 94. Upon oscillation of lever 94, as previously described, the ribbon H0 is fed. in one direction or the other, over guides III and between the typewheel 36 and the tape, as it bends around the end 90b of hammer support 90.

Printing mechanism a tooth Illt of a trigger lever Ill pivoted at Illp. Trigger Ill is biased in a counterclock- Novel printing and printing control mechanism? as shown and described in applicants copending application Serial No. 419,577 filed November 18, 1941 is provided. A reciprocable hammer member 'll2 (Figs. 10 and 11), provided with a printing head ll2a, is mounted forreciprocation in printing hammer support member 90. A threaded member II3 (Fig. 10) threaded into support 90 provides an interiorly located abutting surface ll3a against which rests one end of a coil spring ll2sl surrounding .the hammer II2 and abutting the lugs ll2b, ll2b, integral with hammer II2 and urging hammer head ll2a to engage the tape 81, ribbon H0 and typewheel 36. A pair of opposed shoulders H20 and M (Fig. 11) is also provided on hammer II2. A spring ll2s2 (Fig. 10) surrounds hammer II2 and rides freely between shoulders 20 and I I2d, in the cocked position of hammer ll2, as illustrated in Fig. 10, and the coiled spring extends above and below the flat top and bottom surfaces of hammer head II2a (Fig. 10a). Upon release of the hammer from its cocked position, shoulder lI2c moves spring 282 into engagement with a shoulder 90s (Fig. 10a) of member 90, and the spring 282 is compressed as hammer head ll2a impinges against tape 81 to engage the tape, ribbon IIO and typewheel 36. The compressed spring ll2s2 thereupon exerts its force against shoulder ll2c and moves the released hammer, out of engagement with the tape, to thereby release the tape, ribbon and typewheel.

Hammer II2 is also provided with a latching wise direction by a spring Ills. lug Illa is provided on trigger Ill for releasing the trigger. Bell-crank 5 (Fig. 10) is pivoted .at Hip and is biased'in a counterclockwise direction by spring Ills.

The bell-crank II! is provided at one end of one arm thereof with an operating lug I lia which is engaged by cam roller IIGa of cam Illpmounted for rotation with shaft l3, and at the end of its other arm, bell-crank H5 is provided with a triggering lug Il5b located beneath cylindrical lug II la (Fig. 10) of trigger Ill (see also Fig. 11). Upon rotation 'of 'shaft l3, cam H6 is rotated to engage cam roller Ilia and operating lug Ilia of bell-crank 5, to oscillate the bell-crank ll5 clockwise against the tension of spring IISs, whereby triggering lug II5b engages lug Illa to oscillate trigger Ill clockwise against the force of spring Ills so that tooth Illt of trigger Ill and shoulder ll2e of hammer II2, are released, to release the hammer for movement to the right under of compressed spring ll2sl.

Means are provided to compress the spring II2sI to thereby cock the hammer II2 comprising a cam III mounted for rotation with shaft l3 and cooperating with a roller M on the end of one arm of a bell-crank II8 pivoted directly beneath pivot 52) (Fig. 10). The other end of bell-crank H8 is provided with an operating lug IIBb (Fig. 11) cooperating with one lug ll2b of hammer II2. Bell-crank H8 is spring-biased in a counterclockwise direction in the same manner as bell-crank II5. As shaft l3 rotates, cam H1, in engagement with roller Il8a, oscillates bell-crank ll8 clockwise to engage lub 8b of" its lower arm with a lug ll2b of the hammer II2 whereby the hammer is shifted to the left (Fig. 10) against the force of spring ll2sl, to

.compress this spring and cock the hammer. 'When the hammer is cocked, it assumes the position, as illustrated in Fig. 10, with lug lI2e of the hammer engaging tooth lllt of trigger Ill and the trigger Ill therefore holds the hammer in cocked position until trigger Ill is oscillated clockwise by bell-crank II5, as described above, to release hammer II2 to perform its printing function.

Novel means are also provided for adjusting the degree of effectiveness of the printing hammer during the printing function which determines the clearance between the hammer head Il2a and the typewheel 36 when the hammer is released from its cocked position for impact against the tape to compress the tape and ribbon against the typewheel 36. A micrometer screw 9 (Fig. 3) passes through a hole in the enlarged end l20a of lever I20 and is enaged by a cooperating nut Illa. By adjusting the screw 9, the lever I20 can be oscillated about its pivot I201 (Fig. 10) so that a stop lug l20b (Fig. 11) of lever I20 can be adjusted in position between a lug 211 of hammer II2 and the hammer head ll2a. As lug I201 is moved to the left, as viewed in Fig. 11, the degree of effectiveness or the intensity of impact of the hammer head ll2a, is decreased, but as the position of lug l20b is adjusted to the right, as viewed in Fig. 11, the hammer head ll2a is permitted to approach closer to typewheel 36,

- when harqier II2 is triggered, and the degree A cylindrical the force v General operation While the operations of the various elements of the complete printer have been described in connection with the individual elements, a brief description of the operation of all elements of the device will now be presented in order to clarify the coaction of the relative parts in producing printing of characters upon a tape in response to code signal permutations received, each permutation being representative of a character to be printed or a function to be performed.

It is assumed that the tape 81 has been threaded between tape guide member I06 (Fig. 10) and the end 90b of hammer support 90 and also between the printing hammer head H211 and typewheel 36 and across the face of the printer front panel 26a and between the tape feed rollers, so that-the tape will be automatically fed, step by step, as the printing functions are performed, and the ribbon III] is assumed to be wound from one spool, between the paper tape and typewheel, to the other spool and is ready for its automatic feeding operation.

Upon energization of the motor 2| (Fig. 3) the respective ratchet gears 36 and 33 (Figs. 1 and 2) of the clutches 34 and 3'! are rotated at 1200 R. P. M. and ratchet gear 4| (Fig. 2) of clutch 42 is rotated at 900 R. P. M.

Upon reception of a complete signal, comprising a start element, five signal elements of the signal proper, and a stop element, well known start-stop mechanism is released for rotation in synchronism with the received code signal elements so that the five signal elements of the signal proper, or any permutations thereof, are provided at the receiver, in accordance with the permutations of signal elements received.

Upon reception of the five signal elements.

, comprising a code signal permutation proper, cer

tain of the magnets 50, 5I and 52 (Fig. 3), 53 and 55 (Fig. 4) will be energized. Upon energization of any one of the magnets 50, 5I or 52, the permutation rings 56, 51 and 58 (Fig. 7) will be released by the triggers 62 (Fig. 3) for relative rotation, to align certain of the notches 65 so that a chosen stop element 49 will be permitted to enter the aligned notches, and as the rings are operated to align these notches the stop element, previously aligned, will be cammed out of its notches and dog lift lever 48 will be released and clutch 34 will be engaged by engagement of tooth 4'It (Fig. 1) and the teeth of ratchet gear 30 which, as stated above, is

rotated at 1200 R. P. M. Shaft 35 will therefore be rotated until dog lift lever 48 (Fig. 3) engages the newly aligned stop 49 to thereby rotatively position the clutch 34, shaft 35, and typewheel 36, in accordance with the permutation of code signals controlling the magnets '50, 5I and 52. Similarly, magnets 53 and 55 (Fig. 4) are energized selectively, by the received code signal permutation, and permutation rings I5 and and I6 (Fig. 8) will be relatively rotatively positioned to permit entry of a stop element 49 (Fig. 4 into the newly aligned notches 55, while the previously aligned stop element is cammed out of the notches and dog lift lever 48 is released for further rotation. The associated clutch 31 will be thereupon rotated until the newly selected stop is engaged by dog lift lever 48 and clutch 31 will rotate the cylindrical cam 38 (Fig. 1) to rotatively position it in accordance with the particular permutation of code signal elements controlling magnets 53 and 55.

Rotation of cylindrical cam 38 will axially position the follower I1 and slidable element BI to eb similarly axially position the roller 11a and grooved collar I0 attached to the typewheel 36, to axially position the typewheel in one of four axial positions, to select one of the four horizontal rings of characters (Fig. 2)

Since shaft and typewheel 36 were rota tively positioned to choose one of sixteen uniformly spaced vertical columns of characters and since rotation of cylindrical cam 38 has axially positioned the typewheel to select one of the horizontal rings of characters, one character only will be selectively located in printing position and this character is that one represented by the permutation of 5-code signal elements of the signal received.

Upon energization of magnet 54, which may be designated as the print magnet, its associated clutch 42 (Figs. 2 and 4) will be released for one complete revolution, and since ratchet gear 4| (Fig. 2) which drives clutch 42, rotates at 900 R. P. M., the shaft 43 rotated by clutch 42 will also rotate at this speed.

Since shaft 35 which rotatively positions the typewheel and since cylindrical cam 38 which axially positions the typewheel are both driven at 1200 R. P. M. while shaft 43 is rotated at 900 R. P. M., regardless of which stop elements are selected, the shaft 35 and cylindrical cam 38 will always have completed their rotation and will be halted by the time the shaft 43 has completed three-quarters of a revolution. With the sequential system of signal transmission, as assumed in the instant application, the typewheel will be completely positioned even quicker with respect to the rotation of shaft 43.

As shaft 43 rotates its one complete revolution, the cams attached thereto will be also rotated, in fixed time sequence. The ribbon H0 and tape 81 will be advanced by rotation of disk cam 92 (Figs. 2 and 3), the printing hammer I I2 will be cooked by cam I I1 (Figs. 2 and 10) and the trigger I I4 will be released to cause printing, by operation of cam II6 (Figs. 2 and 10). The intensity of impact of the printing hammer is adjusted by screw II9 (Fig. 3) and the spacing of the characters on the tape is controlled by the particular hole 86b utilized in connecting link to the tape feed lever 96. After printing has been performed, the earns 66 and 66a reset the permutation rings 56, 51, 58, I5 and I5 to the normal position, preparatory to reception of the next code signal permutation, and likewise the lever 6Ib (Fig. 4) controlled by the print magnet 54 will be reset to the position, as indicated in Fig. 4, to engage the dog lift lever 48 and stop the single revolution clutch 42 at the end of its single revolution.

If the code signal permutation is received and is representative of the "figures shift function, the permutation rings will be so positioned that the cylindrical cam 38 will axially locate the typewheel in its extreme lower position and shaft 35 will so rotatively locate the typewheel that lug 'I3bI of slide I3 will be engaged by the operating lug 820 of shift lever 82, when lever 82 is oscillated by roller 86a of cam 86 (Fig. 10) upon rotation of shaft 43. Slide I3 will thereby be shifted to rotate the typewheel 36 one-sixteenth'of a revolution to produce the figures" shift function and the permutation rings will be subsequently reset to normal position and the lever 6Ib of the print magnet 54 to the position, as illustrated Fig. 4, by operation of the reset arms 66 and If the permutation code signal received is representative of the letters shift function, the permutation rings will be so positioned that the typewheel 36 will be located in its extreme upper position and so positioned rotatively that lug 13b on slide 13 will be engaged by operating lug 83c of shift lever 83, upon rotation of shaft 43 and consequent rotation of cam roller 86b on cam 86, to rotate the typewheel one-sixteenth of a revolution to perform the letters shift function. Subsequently, the permutation rings will be returned to normal position and the lever Blb of the print magnet 54 to the position, as indicated in Fig. 4, by means of the reset levers 68 and 68a. In the two shift positions of the typewheel, there are no characters opposite the hammer H2 so that no character-is printed upon the tape 81 during performance of the shift functions.

Novel shift means for finally rotatably shifting a typewheel and for also initially rotatably shifting the typewheel, and locking means for locking both said shift means and said typewheel in either one of two assumed positions are therefore provided, which are extremely simple and highly efiicient.

While there has been shown and described and pointed out the fundamental novel features of the invention as applied to a single embodiment, it will be understood that various omissions and substitutions and changes in the form and details of the device illustrated, and in its operation, may be made by those skilled in the art, without departing from the spirit of the invention. It is the intention, therefore, to be limited only as indicated by the scope of the following claims.

What is claimed is:

1. In a device of the character described, a typewheel, means for initially rotatably positioning said typewheel,and shift means for finally rotatably positioning said typewheel comprising a movable member actuable radially of said typewheel, means cooperating with said initially positioning means for .rotating said movable member, and cooperating means on said typewheel and said movable member effective upon radial movement of said member to finally rotatably adjust said typewheel, said last means also initially rotatably positioning said typewheel upon rotation of said movable member.

2. In. a device of the character described, a

ating means on said typewheel and said movable' member effective upon radial movement of said member to rotate said typewheel from one rotative position to another, and cooperating means on said movable member and said typewheel to hold said movable member in either one of the two assumed radial positions of said movable member, said last-named means also looking said typewheel in either one or the other of said rotative positions.

3. In a device of the character described, a typewheel, means mounting said typewheel for rotativ movement, a slidable member movable radially of said typewheel and means comprising a single projecting element on said radially movable member and a single groove on said typewheel for converting radial movement of said member into rotation of said typewheel.

4. In a device of the character described, a typewheel, means for rotatably positioning said typewheel, means for axially positioning said typewheel, shift means comprising a radially movable member, means operative in one combined axial and rotative position of said typewheel for shifting said movable member in one direction, means operative in another combined different axial and similar rotative position of said typewheel for shifting said movable member in the opposite direction, and cooperating means on said member and said typewheel for converting radial movement of said member into rotative movement of said typewheel in one rotative direction and radial movement of said member in the opposite direction into rotative movement of said typewheel in .the opposite rotative direction.

of saidtypewheel, a first means on said slidable member projecting in one direction, and a second means on said slidable member projecting in the opposite direction, said first projecting means only, cooperating with said first member, in one chosen combined rotative and axial position of said typewheel, to produce sliding movement of said slidable member upon radial movement of said first member, and said second means only, cooperating with said second member, in another chosen combined rotative and axial position of said typewheel, to produce sliding movement of said slidable member upon radial movement of said second member.

6. Ina device of the character described, a typewheel, means for rotatably and axially positioning said typewheel, and means for producing shift of said typewheel comprising a pair of levers, means forming an elongated slot in each lever, means cooperating with the sides of said slots, respectively, for pivotally mounting said levers, means resiliently biasing said levers to position one end of each of said slots against its cooperating pivot, means for oscillating said levers about said pivots, and means cooperating with one of hollow member.

said lever in one combined rotative and axial position of the typewheel to produce shift of said typewheel upon operation of said one lever, and cooperating with the other of said levers, in another combined rotative and axial position of said typewheel, to shift said typewheel upon 05-. cillation of said other lever.

7.-In adevice of the character described, a shaft, 9; typewheel assembly including a hollow cylindrical member mounted on said shaft for rotation with respect thereto, a radially slidable member mounted on said shaft, a slotted member inounted on said shaft adjacent to said slidable member, means on said slidable member cooperating with the sides of said slots in said slotted member to restrain said slidable member to movement of translation, a single protruding element .on said slidable member, means forming a single CLYDE J. FITCH. KURT R. SCHNEIDER. 

